US4035042A - Thrust bearing - Google Patents

Thrust bearing Download PDF

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Publication number
US4035042A
US4035042A US05/668,466 US66846676A US4035042A US 4035042 A US4035042 A US 4035042A US 66846676 A US66846676 A US 66846676A US 4035042 A US4035042 A US 4035042A
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US
United States
Prior art keywords
thrust
bearing
pillar
pad
pillars
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US05/668,466
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English (en)
Inventor
John Black O'Rourke
Peter Gordon Stopp
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Federal Mogul Engineering Ltd
Original Assignee
Glacier Metal Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Glacier Metal Co Ltd filed Critical Glacier Metal Co Ltd
Application granted granted Critical
Publication of US4035042A publication Critical patent/US4035042A/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/04—Sliding-contact bearings for exclusively rotary movement for axial load only
    • F16C17/06—Sliding-contact bearings for exclusively rotary movement for axial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C41/00—Other accessories, e.g. devices integrated in the bearing not relating to the bearing function as such
    • F16C41/02—Arrangements for equalising the load on a plurality of bearings or their elements

Definitions

  • This invention relates to thrust bearings comprising a housing containing an annular ring of thrust pads.
  • each thrust pad is mounted to be capable of tilting on its own thrust pillar, the pillars being located axially against a wall of the bearing housing and circumferentially by a cage ring.
  • the arrangement of the present invention merely uses a cage ring to locate individual thrust pillars circumferentially and they are supported against the thrust loads by the wall of the bearing housing itself, and that represents a considerable economy in the design and manufacture of the thrust bearing.
  • each thrust pillar includes a hydraulic chamber transferring load between the pad and the housing wall, and if the chambers in all the pillars are arranged to be supplied with hydraulic fluid at the same pressure, then each pad can automatically adjust itself in position so that they share the common thrust load equally.
  • the supply of hydraulic fluid to the pillars is conveniently by way of one or more galleries in the cage ring.
  • FIG. 1 is a diagrammatic plan view of a thrust bearing with certain of the thrust pads omitted;
  • FIG. 2 is a view looking in the direction of the arrow Y in FIG. 1;
  • FIG. 3 is a view seen in the direction of the arrow X in FIG. 1;
  • FIG. 4 is a view partly corresponding to FIG. 3 of a modification of the bearing of FIGS. 1 - 3 and also including a hydraulic circuit.
  • the thrust bearing of FIGS. 1, 2 and 3 has an annular series of thrust pads 14 which between them define a generally annular surface which bears load from an annular thrust ring carried by a shaft extending through the centre of the thrust surface when the bearing is in use.
  • Each pad 14 is supported on its own thrust pillar 12 and the thrust pillars themselves are supported directly on the rear wall 13 of the bearing housing, and they are held and located in a circumferentially spaced manner by a cage ring 10 having a series of holes in each of which one of the thrust pillars 12 is a fairly close fit.
  • each thrust pad 14 contains a recess 16 to accommodate the end of the thrust pillar 12 which extends through the cage ring 10, and at the centre of the recess 16 is a radially directed rib 15 whose face contacts the outer face of the thrust pillar so as to allow each thrust pad 14 to tilt in use under load about a radial axis defined by the rib 15. It would be equally possible for the rib to be on the face of the thrust pillar rather than on the rear face of the thrust pad. The rib need not be radially central of the pad.
  • the rear face of the thrust pad is also formed with or fitted with flanges 17 one on either side of the pillar to locate the pad in relation to the pillar circumferentially. If the thrust pad is cast then the flanges 17 can be cast with it. Alternatively they can be separately bolted or welded to the rear face while if as shown at the pad is made from steel plate, a radial recess can be machined in its rear face and the sides 18 of the recess can act as the flanges 17 to locate the pad on the thrust pillar circumferentially.
  • a stop plate 19 is also formed on or secured to the underside of each pad 14 to provide location against the radially inner side of the thrust pillar, and that could engage in an under-cut in the pillar indicated generally at 21 to provide location in an axial direction.
  • the arrangement described is very convenient for a large bearing with a diameter of say a few feet, because it is not necessary to machine the opposed flat faces of the cage ring 10 precisely, and the rear face 13 of the housing is used for axial location of the thrust pads through the medium of the thrust pillars which can be much more easily machined to the correct length.
  • the cage ring merely serves to locate the thrust pillars and each pad can tilt on its thrust pillar just as if it were supported on a conventional thrust ring. It is much simpler to form or machine the rear face 13 of the housing sufficiently precisely to locate the pillars 12 than it is to machine the face of a conventional thrust ring.
  • the thrust collar 22 on the shaft is once again supported on the annular ring of tilting thrust pads 14 and although each of those is seated on its own thrust pillar which in turn is supported from the rear wall 13 of the housing, the construction of the thrust pillar is more complicated than in FIGS. 1, 2 and 3.
  • the pillar comprises an external body 23 which can slide away from the surface 13 on a piston like member 24 seated on the surface 13 and carrying a base plate 25, a hydraulic load cell being indicated generally at 26.
  • the load cell has a hydraulic fluid chamber 27 defined in a recess in the member 23 closed by an elastomeric diaphragm 28 having an external flange 29 which is a close fit in a rebate 31 in the annular wall of the member 23 surrounding the recess 27.
  • the inner face of the diaphragm flange 29 is serrated to provide a good hydraulic seal.
  • the chamber 27 is filled with hydraulic fluid under pressure through a line 32, and any fluid which does leak past the seal 31 can be withdrawn from the space 33 through a line 34.
  • a common source of hydraulic fluid is used to provide fluid to the recesses 27 in all the thrust pillars so that each will have the same load urging the member 23 away from the surface 13 towards the underside of the thrust pad 14, and in that way it can be arranged that each thrust pad automatically takes its equal share of total thrust load.
  • the hydraulic lines 32 and 34 lead to a common pair of galleries 35 and 36 in the cage ring 10 and they are supplied with fluid through a conventional circulating supply system including an air driven hydraulic pump 37, hydraulic accumulators 38, an oil tank 39 to which the return line 34 is connected and a hydraulic pressure guage 41 which is responsive to the supply pressure and so gives a measure of the thrust load being supported. It is believed that a detailed description of that circuit is not necessary.
  • each thrust pillar the load is transmitted between the thrust pad 14 and the housing surface 13 through the load cell since any tendency of pad 14 to move towards the surface 13 is accompanied by a tendancy of the base 25 to squash the diaphragm towards the base of the recess 27 at an annular ring 42 formed by a local corrugation in the wall of the diaphragm.
  • All the thrust cells are identical and since the pressures in them all will be the same, the thrust load supported by each pillar will also be the same and a balanced thrust bearing will be achieved. Once again it has not been necessary to provide a separately machined thrust cage.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sliding-Contact Bearings (AREA)
  • Rolling Contact Bearings (AREA)
  • Support Of The Bearing (AREA)
  • Magnetic Bearings And Hydrostatic Bearings (AREA)
US05/668,466 1975-03-20 1976-03-19 Thrust bearing Expired - Lifetime US4035042A (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
UK11685/75 1975-03-20
GB11685/75A GB1537460A (en) 1975-03-20 1975-03-20 Thrust bearing

Publications (1)

Publication Number Publication Date
US4035042A true US4035042A (en) 1977-07-12

Family

ID=9990811

Family Applications (1)

Application Number Title Priority Date Filing Date
US05/668,466 Expired - Lifetime US4035042A (en) 1975-03-20 1976-03-19 Thrust bearing

Country Status (8)

Country Link
US (1) US4035042A (ja)
JP (1) JPS589844B2 (ja)
CS (1) CS181196B2 (ja)
DE (1) DE2611564A1 (ja)
FR (1) FR2304819A1 (ja)
GB (1) GB1537460A (ja)
IT (1) IT1057430B (ja)
SE (1) SE7603454L (ja)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4168101A (en) * 1978-04-21 1979-09-18 General Electric Company Spring assembly for a high pressure thrust bearing
US4403873A (en) * 1982-01-11 1983-09-13 Waukesha Bearings Corporation Tilting pad thrust bearing
CN113404774A (zh) * 2021-06-10 2021-09-17 湖南崇德科技股份有限公司 一种自平衡推力滑动轴承

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4738550A (en) * 1986-09-08 1988-04-19 Waukesha Bearings Corporation Tilting pad thrust bearing with optimized tilt axis location
DE4021053A1 (de) * 1990-06-29 1992-01-09 Mannesmann Ag Axial-radiallager fuer eine welle
US5205653A (en) * 1991-05-01 1993-04-27 Westinghouse Electric Corp. Bearing assembly and submersible propulsor unit incorporating the same
DE10059196C2 (de) * 2000-11-29 2002-11-07 Sartorius Gmbh Axialgleitlager für rotierende Wellen
KR101514226B1 (ko) * 2010-12-09 2015-04-22 알스톰 르네와블 테크놀로지즈 선박용 터빈 샤프트를 위한 베어링 조립체, 및 이와 같은 베어링 조립체를 구비하는 선박용 터빈

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3142519A (en) * 1962-12-07 1964-07-28 Ind Tectonics Inc Tilting pad thrust bearing
US3154355A (en) * 1963-05-15 1964-10-27 Kingsbury Machine Works Inc Equalizing thrust load between thrust bearings
US3160450A (en) * 1962-11-16 1964-12-08 Mechanical Tech Inc Thrust bearing
US3814487A (en) * 1973-01-08 1974-06-04 Waukesha Bearings Corp Thrust bearing with pad-retaining and lubrication means

Family Cites Families (7)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE312489C (ja) * 1917-01-25
US1836065A (en) * 1926-08-18 1931-12-15 Bbc Brown Boveri & Cie Thrust bearing
US2744799A (en) * 1952-04-23 1956-05-08 Howarth Mary Johnston Bearing
US2871070A (en) * 1955-10-25 1959-01-27 Eustace S Dunn Self-equalizing thrust device
FR1450715A (fr) * 1964-08-19 1966-06-24 Escher Wyss Sa Palier d'arbre avec rotor glissant sur des patins segmentaires orientables
FR1442207A (fr) * 1965-08-09 1966-06-10 Escher Wyss Sa Palier dans lequel le rotor est porté par des patins inclinables
US3588203A (en) * 1969-09-12 1971-06-28 Allis Louis Co Self-equalizing,self-aligning thrust bearing

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3160450A (en) * 1962-11-16 1964-12-08 Mechanical Tech Inc Thrust bearing
US3142519A (en) * 1962-12-07 1964-07-28 Ind Tectonics Inc Tilting pad thrust bearing
US3154355A (en) * 1963-05-15 1964-10-27 Kingsbury Machine Works Inc Equalizing thrust load between thrust bearings
US3814487A (en) * 1973-01-08 1974-06-04 Waukesha Bearings Corp Thrust bearing with pad-retaining and lubrication means

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4168101A (en) * 1978-04-21 1979-09-18 General Electric Company Spring assembly for a high pressure thrust bearing
US4403873A (en) * 1982-01-11 1983-09-13 Waukesha Bearings Corporation Tilting pad thrust bearing
CN113404774A (zh) * 2021-06-10 2021-09-17 湖南崇德科技股份有限公司 一种自平衡推力滑动轴承

Also Published As

Publication number Publication date
SE7603454L (sv) 1976-09-21
FR2304819A1 (fr) 1976-10-15
CS181196B2 (en) 1978-03-31
FR2304819B1 (ja) 1982-10-01
DE2611564A1 (de) 1976-09-30
IT1057430B (it) 1982-03-10
JPS589844B2 (ja) 1983-02-23
JPS51117253A (en) 1976-10-15
GB1537460A (en) 1978-12-29

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